Turbo-compressor-pump

ABSTRACT

A turbo-compressor-pump unit utilizing a common working fluid in the turbine, compressor, pump, and as libricant. A dynamic sealing and bearing means maintains separation of the working fluid at different energy or pressure levels within the turbocompressor-pump unit.

United States Patent 1191 Nichols 1 Apr. 24, 1973 TURBO-COMPRESSOR-PUMP[75] Inventor: Kenneth E. Nichols, Arvada, C010.

[73] Assignee: The Gates Rubber Denver, C010.

[22] Filed: June 22, 1971 21 Appl. No.: 155,497

Company,

[52] US. Cl. ..60/36, 62/402, 184/6.l1 [51] Int. Cl ..F01k 25/00 [58]Field of Search ..184/6.l1; 165/26;

[56] References Cited UNITED STATES PATENTS 3,133,425 5/1964 Hanny etal. ..62/402 X 3,292,366 12/1966 Rice et al. ..60/36 3,105,631 10/1963Hanny 3,568,438 3/ l 971 Meienberg ..60/36 Primary Examiner-Manuel A.Antonakas Attorney--Raymond Fink et a1.

[5 7] ABSTRACT A turbo-compressor-pump unit utilizing a common workingfluid in the turbine, compressor, pump, and as libricant. A dynamicsealing and bearing means maintains separation of the working fluid atdifferent energy or pressure levels within the turbo-compressorpumpunit.

17 Claims, 5 Drawing Figures PAIENIEBAPRM 197s 3728,85?

I I SHEET 1 [IF 2 FIG.2 FIG, VAPOR I GENERATOR E'IVAPORATOF? I N V E NTO F? KENNETH E. NICHOLS FIG. 3 BY mo ATTORNEY 9O\ CONDENSER mmmmm I9153.728.857

' SHEEI 2 UF 2 I N VE. l\| TO R KENNETH E. NICHOLS ATTQRNTURBO-COMPRESSOR-PUMP BACKGROUND OF THE INVENTION The invention relatesto turbine power plants, but more particularly the invention relates toturbine powered pumps or compressors, adapted for use with Rankine cyclepower systems.

The advantages of using a Rankine cycle system as a means of convertingheat energy to work is well recognized. For example, a Rankine cyclesystem may be used to power a refrigeration system. In such systems, it

' is also recognized as being advantageous to use a common working fluidfor the power and refrigeration loops. For thermodynamic reasons, it isdesirable to use a working fluid exhibiting high pressure differentialsat relatively low temperatures in light weight and low power engineapplications. Such working fluids include the halogenated hydrocarbons.Examples of such power systems include U.S. Pat. No. 3,259,176 as issuedto Rice et al., and US. Pat. No. 3,479,817 as issued to Minto.

While the use of a Rankine cycle system in low power applications ishighly desirable, the use thereof invites sealing and lubricationproblems. As previously mentioned, the desirable working fluid mustexhibit high differential pressures at moderate temperatures. Or inother words, the fluids typically have high vapor pressures, nearambient conditions, coupled with low viscosities. The fluidcharacteristics make them susceptible to leakage past even the best typewiping seals. Too much fluid loss results in failure of the powersystem. Replacement of the working fluid is both time consuming anduneconomical.

Lubrication presents another problem. All rotating machinery of thepower system must be properly lubricated. Some systems mix an oil withthe working fluid to effect lubrication. The oil affects the heattransfer characteristics of the heat exchangers used in the system.Other systems have elaborate means to prevent oil from mixing with theworking fluid. Inadvertent oil mixing may also degrade the working fluidto a point that seriously affects thermodynamic efficiency.

SUMMARY OF THE INVENTION In accordance with the invention, aturbo-compressor-pump is provided having internal flow control orsealing means whereby the same working fluid is used in the turbine,pump, compressor, and as lubricant. A rotative shaft has a turbine wheelattached at one end thereof and a compressor wheel attached at theopposite end. A fluid pump is also attached to the shaft. A housing,including appropriate diffusers, inducers, passageways and shroudes,mounts and receives the rotative shaft and the component parts attachedthereto. A bearing, retained or mounted by the housing, supports therotative shaft near each end thereof. A flange having oppositely facingsurfaces projects in a radial manner from the shaft adjacent eachbearing. One side of each flange provides a thrust surface for thebearing adjacent thereto. The opposite side of each flange defines apumping means having a fluid pressure rise capability responsive torotation of the shaft. The pressure of the working fluid exiting thebearings is less than that of pumping means defined on the flanges. Allcomponents mounted to or from the shaft are fluidly communicable viahousing-shaft clearances, and passageways. Thus the same working fluidis exposed to all components on the shaft. Rotation of the shaftactivates the pumping means and bearings to effect separation of theworking fluid at various pressures and conditions between componentsmounted to the shaft.

Accordingly, it is an object of the invention to provide aturbo-compressor-pump unit that utilizes a common working fluid for allrotative components.

Another object of the invention is to provide a turbocompressor or pumpunit which uses a common working fluid for expansion, compression,pressurization and lubrication and where the common fluid is dynamicallyseparated by fluid control means contained within the unit.

A further object of the invention is to provide a hermetically sealableturbo-compressor or pump unit which is free of wiping seals.

Still another object of the invention is to provide a hermeticallysealed Rankine cycle power plant which may be used in combination with ahermetically sealed refrigeration system, together operable with thesame working fluid.

An advantage of the invention is that the turbine working fluid is alsoused as the lubricant for the bearings supporting the turbine shaft. Nolubricating oils are used or required.

These and other objects or advantages of the invention will become moreapparent by reviewing the drawings and description thereof wherein:

FIG. I is a partial cross-sectional view of a turbocompressor-pump ofthe invention.

FIG. 2 is a view taken along the line 2-2 of FIG. 1.

FIG. 3 is a schematic showing the turbo-compressor pump of the inventioninstalled in a Rankine cycle system that powers a refrigeration system.

FIG. 4 is a view similar to FIG. 1 but showing an alternate form of theinvention.

FIG. 5 is a view taken along the line 5-5 of FIG. 4.

DESCRIPTION OF PREFERRED EMBODIMENT Referring to FIGS. 1 and 2, aturbo-compressorpump unit 10 is provided in accordance with theinvention. At one end of a rotative shaft 12 is mounted a radial inflowturbine wheel 14 of known configuration. A plurality of cantileveredturbine blades 16 project from the periphery of one side or face of theturbine wheel 14. An axial flow turbine may be used but the radialinflow type is preferred as it simplifies plumbing and manufacturingproblems. The turbine wheel is disposed within a housing 20. A portionof the housing mounts, retains, or defines at least one nozzle 22 fordirecting'a compressed gaseous working fluid to power the turbine. Thehousing 20 shrouds the turbine wheel 14 to define a turbine 23 have aturbine exhaust 24 for directing expanded gaseous working fluid awayfrom the turbine.

The opposite or second end of the shaft mounts a centrifugal compressorwheel 26 of known configuration. Here, the centrifugal compressor withits radially outward flow characteristics is preferred over an axialflow compressor because of plumbing simplification. A portion of thehousing 20 shrouds the compressor wheel 26 and defines: a compressor 27having an inlet 28 for directing low pressure gaseous working fluid tothe compressor wheel 26; a diffuser 28 and volute 30 for collectingcompressed gaseous working fluid from the compressor wheel; and acompressor exhaust 32 for directing compressed gaseous working fluidaway from the unit. The working faces of the turbine 14 and compressor26 wheels face opposite and away from each other to facilitateinterconnecting plumbing therebetween in a manner which will later beexplained.

The rotative shaft 12 is preferably supported near each end portionthereof by a floating slipper bearing 34, 36. Cups or retainers 38, 40are formed within or retained by the housing for mounting and retainingthe bearings 34, 36. Other bearings such as tilting pad bearings, may beusedfBearings of the floating slipper type are preferred as theycompensate and tolerate for some shaft and component unbalance. Thesealing means of the invention includes a flange 42, 44 or collarextending from the shaft 12 adjacent to one radial side of each floatingslipper bearing 34, 36. One side of each flange defines a face 46, 48for transmitting or receiving thrust. The housing 20 forms similar faces50, 52 adjacent theopposite side of the bearing for receiving ortransmitting end thrust through the floating slipper bearings in knownfashion. The two flanges are oppositely facing, as are the housingfaces, to accommodate thrust loads in each direction; and to retain theshaft within the housing. Preferably, the thrust surfaces 46, 48 facetoward each other as shown to simplify housing construction. On thesecond or oppositely facing face of each flange is formed a pumpimpeller 54, 56. The impellers 54, 56 may have any desired shape toprovide a desired pumping efficiency or pressure ratio. For example, thesecondflange face may be: similar to the thrust face; generallyfrustro-conical; or include vanes 58, 60. The housing 20 shrouds eachpump impeller 54, 56. Together, the housing and impellers define twooppositely facing pumping means 62, 64, the significance of which willlater become apparent.

The housing 20 has or mounts passageways or conduits for directingliquid working fluid to and from each bearing. The passageways may beseparate conduits or included within the housing. Bearing feedpassageways 66, 68 direct the working fluid to the inside diameters ofthe bearings 34, 36 while bearing return passageways 70, 72 directsworking fluid away from the outside diameter of the bearings. In theembodiment shown, working fluid is directed to the shaft 12. An annularclearance between the shaft and housing receives the working fluid anddirects it to the bearings. it is, of course, understood that thebearing feed passageways 66, 68 may directly lead to the bearing 34, 36inside diameters. The annular clearance may be considered as anextension of the bearing feed passageways. Optionally, secondary pumpingmeans 71 may be provided on the shaft for raising the pressure of theworking fluid feeding the bearings. The secondary pumping means 71 maybe a step in the shaft or include vanes. Where bearings other than thatof the floating slipper type are use, the secondary pumping means 71 mayhave to be included to effect separation of the working fluid within thehousing in a manner which will be later explained. As the shaft rotates,the secondary pumping means raises the pressure of that portion ofworking fluid directed to the bearings.

The bearing return passageways 70, 72 direct working fluid away from thebearings. The restriction of the return passageways 70, 72 are ofprimary importance as they pertain to the lubricating and working fluidseparation aspects of the invention. The passageways have pre-determinedrestriction to inhibit working fluid flow through the bearings. Thereturn passageways are directed to a working fluid low pressure area.For example, the passageways 70, 72 may be manifolded 74 to optionallylead to a location by either the turbine wheel or compressor wheel, orother lower pressure area. Although the passageways 7 0, 72 may bedirected to locations near the turbine, or compressor, care must beexercised in choosing the location to avoid seriously affecting theoperating characteristics of the turbine or compressor.

Also provided on and extending from the shaft is a feed pump 76 forsupplying high pressure working fluid. The pump is of a special designwhich precludes cavitation at high rotational speeds (e.g., 20,000 to50,000 rpm) as induced by the turbine. The pump 76 requires lessnet-positive-suction-head (NPSl-l) than conventional two stage pumps.The pump has two stages. Two first stage elements supply working fluidto a single second stage impeller. The two first stage elements includetwo oppositely spiraled inducers 78, 80 as upraised vanes extending fromthe shaft 12. The two first stage inducers 78, 80 operate to convergeand supply working fluid to the single, second-stage impeller. If onlyone first stage inducer were provided, net-positive-suction head to thepump may have to be increased as much as 40 percent. The second stageimpeller includes a plurality of vanes 82 radially mounted to orextending from the shaft 12. Working fluid flowing to the pump 76 issplit with the bearing feed passageways 66, 68. The housing defines apump discharge passageway 84 for directing pressurized working fluidaway from the pump.

The housing 20 has heretofore been defined as having characteristics orconfigurations that are complementary to the turbine, compressor, pumpand seals. The housing may consist of a number of direct or separateparts as desired which are fastened or joined together with appropriatefasteners and fittings. In any desired configuration, the housingcompletely and appropriately shrouds the shaft and the componentsmounted thereon. The turbine, bearings, pumps, and compressor arefluidly communicable with each other, under static conditions, throughthe clearances of the housing. No shaft wiping seals or static seals areprovided or are necessary. There is no dynamic seal between any of therotative parts and atomsphere. Thus, the unit as provided ishermetically scalable when the passageways, conduits, and openings ofthe housing are connected with other component parts of a thermodynamicsystem such as a Rankine cycle power plant and refrigeration system.

Here it should be noted with emphasis and particularity that a commonworking fluid is used for the turbine, pumps, compressor, and lubricant.Examples of working fluids capable of performing all functions-includethe halogenated hydrocarbons such as trichloromonofluoromethane,dichlorodifluoromethane, dichlorotetrafluoroethane,

chlorodifluoromethane carbon tetrachloride tricholorotrifluorethane, ormixtures thereof. The working fluid may completely fill all voids orcavities of the unit. Hence, the static pressure throughout the unit isconstant; for example, the pressure may be 8 psia when the turbine isnot rotating. Activation of the unit results in the working fluid beingseparated in a controlled manner into different pressure or energylevels between the turbine, pumps, and compressor. The separation of theworking fluid may best be understood when the unit is installed tooperate with a refrigeration system.

Referring now to FIGS. 1 and 3, the unit 10 is shown schematicallyinstalled with a closed loop refrigeration system. All plumbingconnections to the unit 10 are hermetic. Placement of the feed pump 76within the housing and on the same shaft as the turbine 23 permits thefeed pump to also be hermetically sealed.

The main system components other than the unit of the invention,include: a boiler or vapor generator 88 for vaporizing and heatingworking fluid, such as a fluorocarbon; a condenser 90 for liquifyingpressurized working fluid; expansion means 92 for controllably reducingthe pressure of the working fluid; and an evaporator 94 for vaporizingthe low pressure liquid working fluid and effecting refrigeration. Theunit 10 is hermetically connected in the system 86 with appropriateplumbing. For the purpose of illustration, let it be assumed that thecomponents have generally the following steady state operating pressuresand working fluid phases: vapor generator, 335 psia, vapor; condenser,psia, saturated liquid; and evaporator, 3 psia, vapor.

When the turbine 26 is activated by supplying pressurized gaseousworking fluid to the turbine nozzle 22, for example, gas from the boiler88 at 335 psia, the shaft 12 rotates. The gas expands to a lowerpressure as it passes through the turbine 23. For example, the gas isexpanded to a pressure near that of the condenser, or 20 psia. Duringstart-up, any liquid near the turbine wheel 14 or exhaust 24 isdispelled to the condenser 90. Pressure behind the turbine wheel will beslightly higher than the turbine exhaust pressure; for example, thepressure may be 25 psia.

Rotation of the shaft 12 activates the compressor 27. Any liquid in thearea of the compressor is pumped and dispelled through the compressorexhaust 32 as the compressor strives to compress a gaseous working fluidfrom the evaporator 94, The compressor 27 compresses the gaseous workingfluid and raises the pressure thereof from the 3 psia of the evaporator94 to slightly higher than the 20 psia of the condenser 90.

Simultaneously as the shaft is rotated, liquifled working fluid flowsfrom the condenser 90 at 20 psia andenters the combination bearing andpump feed passageways 66, 68 where the flow is split. A portion of fluidflowing through the passageways is directed to the secondary pumpingmeans 70 where pressure is increased before the fluid enters the insidediameter of the bearings 34, 36. Pressure may be increased from 20 psiato 40 psia, for example. Working fluid then enters the bearings 34, 36at 40 psia and exits the bearings at 60 psia when the shaft reachesnominal speed. Working fluid pressure increases as it flows through thebearing because the rotational motion of the shaft and flanges inducesthe individual pads of the slipper bearings 34,

36 to rotate at a fractional speed of the shaft and increase the workingfluid pressure level. Working fluid exits the bearing through thebearing return passageways 70, 72 and manifolded 74 into the volutecollector of the compressor. The bearing return passageways '70, 72 mayoptionally be manifolded 75 to the turbine 23. Simultaneously workingfluid pressure increases in the oppositely facing pumping means 62, 64.As there is no liquid working fluid feeding the inlet side of theoppositely facing pumping means from either the compressor or turbineside, a free liquid surface is generated which moves radially outwardalong the face of each pump impeller 54,56. When the pump means adjacenteach bearing is initially full of lubricant, each pumping means may havea design pressure rise near 135 psia, which results in an exit pressureof 160 psia. As the free liquid surface of working fluid moves up theface of each pump impeller 54, 56, the exit pressure of each pumpingmeans 62, 64 is correspondingly reduced. Movement of the free liquidsurface along each impeller stops when the exit pressure of each pumpingmeans just equals the exit pressure of the working fluid from thebearings. That is when all four pressures (two bearings 34, 36 and twopumping means 62, 64) are 60 psia. Should the lubricant pressures fromthe bearings increase, the free liquid surface moves radially inward toa point where a pressure balance is achieved. Thus, it is seen that thepumping means ad- 30 jacent the turbine may seal at a different pressurefrom that of the pumping means adjacent the compressor. In the instantexample, the bearing exit pressures could reach 160 psia and a dynamicseal would still be maintained.

That working fluid flowing through the bearing feed passageways thatdoes not flow to the bearings, flows to the two first stage inducersections 78, of the feed pump 76. The two inducer sections 78, 80 raisethe pressure of the working fluid an amount to prevent cavitation of thesecond stage of the pump. For example, the inducer stage may raise thepressure from 20 psia to 40 psia. The two first stage inducer sectionspermit the second stage of the pump to operate at high rotational speedswithout cavitating. The second or main stage 82 of the pump raises thepressure of the working fluid to a pressure level near that of theboiler, or 335 psia, the working fluid is then discharged from the pump76 to the boiler 88.

The foregoing example is illustrative of the many advantages of theinvention, Summarily, the same working fluid is used for the turbine,compressor and lubricant. By using the working fluid as a lubricant, theneed for static or wiping seals is eliminated. it is unnecessary toprovide a lubricant separate from or carried along with the workingfluid. As the feed pump is mounted to the same shaft as the turbine, noseparate prime mover or sealing or lubrication arrangement is needed forthe pump. 1

ADDITIONAL SPECIES The foregoing embodiment uses floating slipperbearings to support the rotative shaft. Floating slipper bearings arepreferred as they tolerate and adjust for a dynamic unbalance of therotative elements which would be untolerable for other types ofbearings. However, floating slipper bearings are not required to realizethe benefits of the invention as other bearings may be used while stillmaintaining separation and control of the working fluid under dynamicconditions. Referring now to FIGS. 4 and 5, a turbo-compressor-pump unit96 similar to that of FIGS. 1 and 2 is shown. The elements of the unitare the same except for the bearing system. The rotative shaft 12 isradially supported by two tilting pad bearings 98, 100, each bearingincluding a plurality of individual pads 102 encircling the shaft andpivotally 104 supported from the housing 20. The bearings radiallysupport the shaft in known fashion. A thrust collar or ring 106, 108extends radially inward from the housing adjacent the thrust face 46, 48of each flange extending from the shaft. A spiral groove,

not shown, in either the thrust washer or flange may be provided tochannel a sufficient amount of working I fluid for lubrication. As thetilting pad bearings do not perform a pumping action like the floatingslipper bearings, the pressure rise capability of the secondary pumpingmeans 71 may have to be increased, or that of the pumping means 62 64decreased, to effect desired dynamic sealing. For example, the pressurerise capability of the secondary pumping 70 means may be increased from40 psia to 60 psia. Sealing and separation of the working fluid withinthe unit is then the same as previously explained.

The foregoing detailed description is made for purpose of illustrationonly and is not intended to limit the scope of the invention which is tobe determined from the appended claims.

What is claimed is:

1. In a turbo-compressor unit of the type operative with a vaporizedworking fluid and having a turbine and compressor wheel mounted to amutual rotative shaft that is supported by a first bearing near theturbine wheel and a second bearing near the compressor wheel and wherethe shaft, turbine wheel, compressor wheel and bearings are mountedwithin a housing, the improvement which comprises:

a first passageway disposed within the housing, and directed to eachbearing, said first passageway capable of supplying liquid working fluidpast each bearing at a pressure;

a first pumping means disposed within the housing between the firstbearing and turbine for pressurizing working fluid to a pressure justequal to the pressure of the working fluid past the first bearing fromsaid first passageway, said first pumping means responsive to rotationof the shaft and having a pump inlet and outlet, the pump inlet beingfluidly communicable with the turbine and the pump outlet being fluidlycommunicable with said first passageway past the first bearing;

a second pumping means disposed within the housing between the secondbearing andcompressor for pressurizing working fluid to a pressure justequal to the pressure of the working fluid past the second bearing fromsaid first passageway, said second pumping means responsive to rotationof the shaft and having a pump inlet and outlet, the pump inlet beingfluidly communicable with the compressor and the pump outlet beingfluidly communicable with said first passageway past the second bearing;and

a second passageway disposed within the housing and directed from theoutlet of said first and second pumping means for channeling workingfluid from said first passageway, first and second bearings, and firstand second pumping means, said second passageway having a pre-determinedrestriction for limiting working fluid flow therethrough.

2. A turbo-compressor unit as set forth in claim 1 and furtherincluding:

a third pumping means disposed within the housing and mounted to therotative shaft for pressurizing working fluid to the bearings inresponse to rotation of the shaft, said third pumping means having apump inlet and outlet manifolded in series with said first passageway.

3. A turbo-compressor as set forth in claim 1 and further including:

a fourth pumping means disposed within the housing and mounted to therotative shaft for supplying pressurized working fluid external of theturbo compressor unit, said fourth pumping means having a pump inletmanifolded to said first passageway.

4. A turbo-compressor as set forth in claim 3 wherein said fourthpumping means comprises:

a first stage inducer section including two oppositely spiraled vanesprojecting from the shaft at a location between the bearings, said firststage inducer section manifolded to said first passageway; and

a second stage impeller mounted to said shaft between the two oppositelyspiraled vanes, said second stage impeller including a plurality ofvanes projecting generally radially from the shaft.

5. In a turbo-compressor unit of the type operative with a vaporizedworking fluid and having a turbine and compressor wheel mounted to amutual rotative shaft that is supported by a first bearing near theturbine wheel and a second bearing near the compressor wheel, and whereall of which are disposed and mounted within a housing, a method oflubricating the bearings with the same working fluid whilesimultaneously dynamically separating the working fluid between theturbine, compressor and bearings, comprising the steps of:

flowing liquified working fluid under pressure past the bearings;

balancing the pressure of the liquified working fluid from the firstbearing against the discharge pressure of a first pumping meansresponsive to rotation of the shaft and disposed between the firstbearing and turbine wheel, the first pumping means having a pressurerise capability greater than the pressure of the liquified working fluidflowing from the first bearing;

simultaneously balancing the pressure of the liquified working fluidfrom the second bearing against the discharge pressure of a secondpumping means responsive to rotation of the shaft and disposed betweenthe second bearing and compressor wheel, the second pumping means havinga pressure rise capability greater than the pressure of the liquifiedworking fluid flowing from the second bearing;

manifolding the inlet of the first pumping means to the turbine, whilesimultaneously manifolding the inlet of the second pumping means to thecompressor; and

draining the combined flow of liquified working fluid from the firstpumping means and bearing, and the second pumping means and bearingthrough at least one restriction of pre-determined resistance.

6. The method as set forth in claim and further including the step of:

manifolding the liquified working fluid flow from the bearings to thecompressor.

7. The method as set forth in claim 5 and further including the step of:

manifolding the liquified working fluid flow from the bearings to theturbine. 8. The method as set forth in claim 5 wherein the liquifiedfluid flowing to the bearings is pressurized by a pumping meansresponsive to rotation of the shaft.

9. A hermetically scalable turbo-compressor-pump for use with a mutualworking fluid, comprising;

a rotative shaft having first and second end portions;

a turbine wheel mounted to and near one end portion of said shaft;

a compressor wheel mounted to and near the opposite end portion of saidshaft;

a first flange extending from said shaft near said turbine wheel, saidfirst flange having oppositely facing first and second faces, the facenearest said turbine wheel defining a pump impeller and the other facedefining a thrust surface;

a second flange extending from said shaft near said compressor wheel,said second flange having oppositely facing first and second faces, theface nearest said compressor defining a pump impeller and the other facedefining a thrust surface;

bearing means near the thrust surface of the first and second flangesfor supporting said shaft, said bearing means having inside and outsidediameters;

a housing having a bore that receives said shaft and having retainersfor receiving said bearing means; said housing: shrouding said turbinewheel to define a turbine, shrouding said compressor wheel to define acompressor, and shrouding the pump impeller faces of said first andsecond flanges to define first and second pumping means whichindividually have a desired pressure rise capability;

a third pumping means extending from said shaft and disposed within saidhousing for pressurizing a portion of working fluid, said third pumpingmeans fluidly communicable with and having a pressure rise capabilityless than the pressure rise capability of said first and second pumpingmeans, said third pumping means capable of pumping a portion of workingfluid to near the inside diameter of said bearing means;

a first fluid passageway directed to said third pumping means; and

a second and third fluid passageway directed from said first and secondpumping means, said second and third passageways having predeterminedrestriction for limiting flow of working fluid through the bearings.

10. A turbo-compressor-pump as set forth in claim 9 and furtherincluding a high speed pump disposed within said housing and mounted tosaid shaft, said high speed pump comprising:

a second stage impeller including a plurality of vanes projectingradially away from said shafts; and

a first stage inducer including a first and second oppositely spiraledvanes projecting in a helical manner away from said shaft, said firstand second spiraled vanes sandwiching said second stage impellertherebetween.

11. A turbo-compressor-pump as set forth in claim 9 and furtherincluding a fourth passageway that manifolds and connects said secondand third passageways with said compressor.

12. A turbocompressor as set forth in claim 9 and further including afourth passageway that manifolds and fluidly connects said second andthird passageways with said turbine.

13. A turbo-compressor as set forth in claim 9 wherein said bearingmeans are floating slipper bearings capable of pumping in response torotation of said shaft to define a pressure rise capability, and whereinthe combined pressure rise capability of said bearings and said thirdpumping means is less than the pressure rise capability of said firstand second pump ing means.

14. In a turbo-compressor unit of the type operative with a singlevaporized working fluid and having a turbine driving a compressor with acommon shaft that is supported a first bearing near the turbine and asecond bearing near the compressor and having a common housing, theimprovement which comprises:

means for flowing a portion of the same working fluid in liquified formunder pressure to and past the bearings to lubricate the bearings;

means for restricting the liquified working fluid flowing as a lubricantfrom the bearings;

means for separating within the housing the vaporized working fluid ofthe turbine and compressor from the fluid flowing past the bearings; and

means for directing the liquid working fluid flowing past the bearingsto the vaporized working fluid of the turbo-compressor unit;

whereby a mutual working fluid is used for lubricating the bearings andin operating the turbine and compressor.

15. A refrigeration system for cooling of the type having a vaporgenerator containing a working fluid,

means for adding heat to the vapor generator to.

vaporize said liquid, a turbine, means for conducting gas from the vaporgenerator to the turbine, a compressor driven by the turbine through amutual shaft, a condenser for receiving and liquifying the vaporizedworking fluid from the turbine and compressor, expansion means forreceiving and controllably decreasing the pressure of the working fluidfrom the outlet of the condenser, an evaporator for receiving andvaporizing the discharge of liquified working fluid from the expansionmeans, wherein the improvement comprises:

a mutual housing shrouding and mounting the turbine, compressor andmutual shaft;

a pump disposed within the housing and mounted to the shaft, said pumpreceiving liquified working fluid from the condenser and dischargingpressurized working fluid into the vapor generator;

bearing means operative with liquified working fluid from the condenserfor rotatively supporting the shaft, means for channeling a portion ofthe same working fluid in liquid form to and from the bearing means;means for separating, within the housing, the

vaporized working fluid of the turbine and compressor from the liquifiedworking fluid of said pump and bearings; and means for directing theliquid working fluid flowing past the bearings to vaporized workingfluid contained within the housing; whereby a hermetically sealedrefrigeration system is provided. 16. In a turbo-compressor unit of thetype operative with a single vaporized working fluid and having aturbine driving a compressor with a common shaft that is supported by afirst bearing near the turbine and a second bearing near the compressorand having a common housing, the improvement which comprises:

means for flowing liquified working fluid under pressure to and past thebearings to lubricate the bearings; means for restricting the liquifiedworking fluid flowing as a lubricant from the bearings; and means forseparating within the housing the vaporized working fluid of the turbineand compressor and the fluid flowing past the bearings, said separatingmeans including a first pumping means disposed within the housingbetween the first bearing and turbine for pressurizing liquified workingfluid to a pressure equal to the pressure past the first bearing fromsaid flowing means, said first pumping means responsive to rotation ofthe shaft and having a pump inlet and outlet, the pump inlet beingfluidly communicable with the turbine and the pump outlet being fluidlycommunicable with said restricting means; and a second pumping meansdisposed within the housing between the second bearing and compressorfor pressurizing liquified working fluid to a pressure equal tothepressure past the second bearing from said flowing means, said secondpumping means responsive to rotation of the shaft'and having a pumpinlet and outlet, the pump inlet being fluidly communicable with thecompressor and the pump outlet being fluidly communicable with saidrestricting means; whereby a mutual working fluid is used forlubricating the bearings and in operating the turbine and compressor.

17. A refrigeration system for cooling of the type having a vaporgenerator containing a working fluid, means for adding heat to the vaporgenerator to vaporize said liquid, a turbine, means for conducting gasfrom the vapor generator to the turbine, a compressor driven by theturbine through a mutual shaft, a condenser for receiving and liquifyingthe vaporized working fluid from the turbine and compressor, expansionmeans for receiving and controllably decreasing the pressure of theworking fluid from the outlet of the condenser, an evaporator forreceiving and vaporizing the discharge of liquified working fluid fromthe expansion means, wherein the imlprovement comprises:

a mutual housing s roudmg and mounting the turbine compressor and mutualshaft;

a pump disposed within the housing and mounted to the shaft, said pumpreceiving liquified working fluid from the condenser and dischargingpressurized working fluid into the vapor generator;

bearing means operative with liquified working fluid from the condenserfor rotatively supporting the shaft, said bearing means including afirst bearing located near the turbine and a second bearing located nearthe compressor;

means for channeling liquified working fluid to and from the bearingmeans;

means for separating, -within the housing, the

vaporized working fluid of the turbine and compressor from the liquifiedworking fluid of said pump and said bearings, said separating meansincluding:

means for restricting flow of liquified working fluid from;

a first pumping means disposed within the housing between the firstbearing and turbine for pressurizing liquified working fluid to apressure equal to the liquified, working fluid at the first bearing,said first pumping means responsive to rotation of the shaft and havinga pump inlet and outlet, the pump inlet being fluidly communicable withthe turbine and the pump outlet being fluidly communicable with thechanneling means of the bearing; and

a second pumping means disposed within the housing between the secondbearing and compressor for pressurizing liquified working fluid to apressure equal to the liquified working fluid at the second bearing,said second pumping means responsive to rotation of the shaft and havinga pump inlet and outlet, the pump inlet being fluidly communicable withthe compressor and the pump outlet being fluidly communicable with thechanneling means of the bearing;

whereby a hermetically sealed refrigeration system is provided.

1. In a turbo-compressor unit of the type operative with a vaporizedworking fluid and having a turbine and compressor wheel mounted to amutual rotative shaft that is supported by a first bearing near theturbine wheel and a second bearing near the compressor wheel and wherethe shaft, turbine wheel, compressor wheel and bearings are mountedwithin a housing, the improvement which comprises: a first passagewaydisposed within the housing, and directed to each bearing, said firstpassageway capable of supplying liquid working fluid past each bearingat a pressure; a first pumping means disposed within the housing betweenthe first bearing and turbine for pressurizing working fluid to apressure just equal to the pressure of the working fluid past the firstbearing from said first passageway, said first pumping means responsiveto rotation of the shaft and having a pump inlet and outlet, the pumpinlet being fluidly communicable with the turbine and the pump outletbeing fluidly communicable with said first passageway past the firstbearing; a second pumping means disposed within the housing between thesecond bearing and compressor for pressurizing working fluid to apressure just equAl to the pressure of the working fluid past the secondbearing from said first passageway, said second pumping means responsiveto rotation of the shaft and having a pump inlet and outlet, the pumpinlet being fluidly communicable with the compressor and the pump outletbeing fluidly communicable with said first passageway past the secondbearing; and a second passageway disposed within the housing anddirected from the outlet of said first and second pumping means forchanneling working fluid from said first passageway, first and secondbearings, and first and second pumping means, said second passagewayhaving a pre-determined restriction for limiting working fluid flowtherethrough.
 2. A turbo-compressor unit as set forth in claim 1 andfurther including: a third pumping means disposed within the housing andmounted to the rotative shaft for pressurizing working fluid to thebearings in response to rotation of the shaft, said third pumping meanshaving a pump inlet and outlet manifolded in series with said firstpassageway.
 3. A turbo-compressor as set forth in claim 1 and furtherincluding: a fourth pumping means disposed within the housing andmounted to the rotative shaft for supplying pressurized working fluidexternal of the turbo compressor unit, said fourth pumping means havinga pump inlet manifolded to said first passageway.
 4. A turbo-compressoras set forth in claim 3 wherein said fourth pumping means comprises: afirst stage inducer section including two oppositely spiraled vanesprojecting from the shaft at a location between the bearings, said firststage inducer section manifolded to said first passageway; and a secondstage impeller mounted to said shaft between the two oppositely spiraledvanes, said second stage impeller including a plurality of vanesprojecting generally radially from the shaft.
 5. In a turbo-compressorunit of the type operative with a vaporized working fluid and having aturbine and compressor wheel mounted to a mutual rotative shaft that issupported by a first bearing near the turbine wheel and a second bearingnear the compressor wheel, and where all of which are disposed andmounted within a housing, a method of lubricating the bearings with thesame working fluid while simultaneously dynamically separating theworking fluid between the turbine, compressor and bearings, comprisingthe steps of: flowing liquified working fluid under pressure past thebearings; balancing the pressure of the liquified working fluid from thefirst bearing against the discharge pressure of a first pumping meansresponsive to rotation of the shaft and disposed between the firstbearing and turbine wheel, the first pumping means having a pressurerise capability greater than the pressure of the liquified working fluidflowing from the first bearing; simultaneously balancing the pressure ofthe liquified working fluid from the second bearing against thedischarge pressure of a second pumping means responsive to rotation ofthe shaft and disposed between the second bearing and compressor wheel,the second pumping means having a pressure rise capability greater thanthe pressure of the liquified working fluid flowing from the secondbearing; manifolding the inlet of the first pumping means to theturbine, while simultaneously manifolding the inlet of the secondpumping means to the compressor; and draining the combined flow ofliquified working fluid from the first pumping means and bearing, andthe second pumping means and bearing through at least one restriction ofpre-determined resistance.
 6. The method as set forth in claim 5 andfurther including the step of: manifolding the liquified working fluidflow from the bearings to the compressor.
 7. The method as set forth inclaim 5 and further including the step of: manifolding the liquifiedworking fluid flow from the bearings to the turBine.
 8. The method asset forth in claim 5 wherein the liquified fluid flowing to the bearingsis pressurized by a pumping means responsive to rotation of the shaft.9. A hermetically sealable turbo-compressor-pump for use with a mutualworking fluid, comprising; a rotative shaft having first and second endportions; a turbine wheel mounted to and near one end portion of saidshaft; a compressor wheel mounted to and near the opposite end portionof said shaft; a first flange extending from said shaft near saidturbine wheel, said first flange having oppositely facing first andsecond faces, the face nearest said turbine wheel defining a pumpimpeller and the other face defining a thrust surface; a second flangeextending from said shaft near said compressor wheel, said second flangehaving oppositely facing first and second faces, the face nearest saidcompressor defining a pump impeller and the other face defining a thrustsurface; bearing means near the thrust surface of the first and secondflanges for supporting said shaft, said bearing means having inside andoutside diameters; a housing having a bore that receives said shaft andhaving retainers for receiving said bearing means; said housing:shrouding said turbine wheel to define a turbine, shrouding saidcompressor wheel to define a compressor, and shrouding the pump impellerfaces of said first and second flanges to define first and secondpumping means which individually have a desired pressure risecapability; a third pumping means extending from said shaft and disposedwithin said housing for pressurizing a portion of working fluid, saidthird pumping means fluidly communicable with and having a pressure risecapability less than the pressure rise capability of said first andsecond pumping means, said third pumping means capable of pumping aportion of working fluid to near the inside diameter of said bearingmeans; a first fluid passageway directed to said third pumping means;and a second and third fluid passageway directed from said first andsecond pumping means, said second and third passageways havingpredetermined restriction for limiting flow of working fluid through thebearings.
 10. A turbo-compressor-pump as set forth in claim 9 andfurther including a high speed pump disposed within said housing andmounted to said shaft, said high speed pump comprising: a second stageimpeller including a plurality of vanes projecting radially away fromsaid shaft; and a first stage inducer including a first and secondoppositely spiraled vanes projecting in a helical manner away from saidshaft, said first and second spiraled vanes sandwiching said secondstage impeller therebetween.
 11. A turbo-compressor-pump as set forth inclaim 9 and further including a fourth passageway that manifolds andconnects said second and third passageways with said compressor.
 12. Aturbo-compressor as set forth in claim 9 and further including a fourthpassageway that manifolds and fluidly connects said second and thirdpassageways with said turbine.
 13. A turbo-compressor as set forth inclaim 9 wherein said bearing means are floating slipper bearings capableof pumping in response to rotation of said shaft to define a pressurerise capability, and wherein the combined pressure rise capability ofsaid bearings and said third pumping means is less than the pressurerise capability of said first and second pumping means.
 14. In aturbo-compressor unit of the type operative with a single vaporizedworking fluid and having a turbine driving a compressor with a commonshaft that is supported a first bearing near the turbine and a secondbearing near the compressor and having a common housing, the improvementwhich comprises: means for flowing a portion of the same working fluidin liquified form under pressure to and past the bearings to lubricatethe bearings; Means for restricting the liquified working fluid flowingas a lubricant from the bearings; means for separating within thehousing the vaporized working fluid of the turbine and compressor fromthe fluid flowing past the bearings; and means for directing the liquidworking fluid flowing past the bearings to the vaporized working fluidof the turbo-compressor unit; whereby a mutual working fluid is used forlubricating the bearings and in operating the turbine and compressor.15. A refrigeration system for cooling of the type having a vaporgenerator containing a working fluid, means for adding heat to the vaporgenerator to vaporize said liquid, a turbine, means for conducting gasfrom the vapor generator to the turbine, a compressor driven by theturbine through a mutual shaft, a condenser for receiving and liquifyingthe vaporized working fluid from the turbine and compressor, expansionmeans for receiving and controllably decreasing the pressure of theworking fluid from the outlet of the condenser, an evaporator forreceiving and vaporizing the discharge of liquified working fluid fromthe expansion means, wherein the improvement comprises: a mutual housingshrouding and mounting the turbine, compressor and mutual shaft; a pumpdisposed within the housing and mounted to the shaft, said pumpreceiving liquified working fluid from the condenser and dischargingpressurized working fluid into the vapor generator; bearing meansoperative with liquified working fluid from the condenser for rotativelysupporting the shaft, means for channeling a portion of the same workingfluid in liquid form to and from the bearing means; means forseparating, within the housing, the vaporized working fluid of theturbine and compressor from the liquified working fluid of said pump andbearings; and means for directing the liquid working fluid flowing pastthe bearings to vaporized working fluid contained within the housing;whereby a hermetically sealed refrigeration system is provided.
 16. In aturbo-compressor unit of the type operative with a single vaporizedworking fluid and having a turbine driving a compressor with a commonshaft that is supported by a first bearing near the turbine and a secondbearing near the compressor and having a common housing, the improvementwhich comprises: means for flowing liquified working fluid underpressure to and past the bearings to lubricate the bearings; means forrestricting the liquified working fluid flowing as a lubricant from thebearings; and means for separating within the housing the vaporizedworking fluid of the turbine and compressor and the fluid flowing pastthe bearings, said separating means including a first pumping meansdisposed within the housing between the first bearing and turbine forpressurizing liquified working fluid to a pressure equal to the pressurepast the first bearing from said flowing means, said first pumping meansresponsive to rotation of the shaft and having a pump inlet and outlet,the pump inlet being fluidly communicable with the turbine and the pumpoutlet being fluidly communicable with said restricting means; and asecond pumping means disposed within the housing between the secondbearing and compressor for pressurizing liquified working fluid to apressure equal to the pressure past the second bearing from said flowingmeans, said second pumping means responsive to rotation of the shaft andhaving a pump inlet and outlet, the pump inlet being fluidlycommunicable with the compressor and the pump outlet being fluidlycommunicable with said restricting means; whereby a mutual working fluidis used for lubricating the bearings and in operating the turbine andcompressor.
 17. A refrigeration system for cooling of the type having avapor generator containing a working fluid, means for adding heat to thevapor generator to vaporize said liquid, a turbine, means for conductinggas from the vapor generator to the turbine, a compressor driven by theturbine through a mutual shaft, a condenser for receiving and liquifyingthe vaporized working fluid from the turbine and compressor, expansionmeans for receiving and controllably decreasing the pressure of theworking fluid from the outlet of the condenser, an evaporator forreceiving and vaporizing the discharge of liquified working fluid fromthe expansion means, wherein the improvement comprises: a mutual housingshrouding and mounting the turbine compressor and mutual shaft; a pumpdisposed within the housing and mounted to the shaft, said pumpreceiving liquified working fluid from the condenser and dischargingpressurized working fluid into the vapor generator; bearing meansoperative with liquified working fluid from the condenser for rotativelysupporting the shaft, said bearing means including a first bearinglocated near the turbine and a second bearing located near thecompressor; means for channeling liquified working fluid to and from thebearing means; means for separating, within the housing, the vaporizedworking fluid of the turbine and compressor from the liquified workingfluid of said pump and said bearings, said separating means including:means for restricting flow of liquified working fluid from; a firstpumping means disposed within the housing between the first bearing andturbine for pressurizing liquified working fluid to a pressure equal tothe liquified working fluid at the first bearing, said first pumpingmeans responsive to rotation of the shaft and having a pump inlet andoutlet, the pump inlet being fluidly communicable with the turbine andthe pump outlet being fluidly communicable with the channeling means ofthe bearing; and a second pumping means disposed within the housingbetween the second bearing and compressor for pressurizing liquifiedworking fluid to a pressure equal to the liquified working fluid at thesecond bearing, said second pumping means responsive to rotation of theshaft and having a pump inlet and outlet, the pump inlet being fluidlycommunicable with the compressor and the pump outlet being fluidlycommunicable with the channeling means of the bearing; whereby ahermetically sealed refrigeration system is provided.